CN104421149B - Changeable flow hydraulic machine - Google Patents
Changeable flow hydraulic machine Download PDFInfo
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- CN104421149B CN104421149B CN201410450027.0A CN201410450027A CN104421149B CN 104421149 B CN104421149 B CN 104421149B CN 201410450027 A CN201410450027 A CN 201410450027A CN 104421149 B CN104421149 B CN 104421149B
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C2/00—Rotary-piston engines
- F03C2/08—Rotary-piston engines of intermeshing-engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
- F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
- F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F01C1/18—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
- F01C20/18—Control of, monitoring of, or safety arrangements for, machines or engines characterised by varying the volume of the working chamber
- F01C20/22—Control of, monitoring of, or safety arrangements for, machines or engines characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C2/00—Rotary-piston engines
- F03C2/02—Rotary-piston engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/18—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/086—Carter
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/18—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber
- F04C28/22—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
Abstract
This application discloses a kind of changeable flow hydraulic machine.More particularly to a kind of changeable flow outer rotor hydraulic machine (10,10 ') of the application, it has：Import (26,26 ')；Export (28,28 ')；Rotor set, the rotor set has for the first rotor (58,58 ') rotated around the first rotor axis and the second rotor for being rotated around the second rotor axis (68,68 '), machine is arranged to pump or motor, wherein, in first and second rotor axis it is at least one can relative to another motion, to change the leakage flow between rotor.
Description
Technical field
The present invention relates to a kind of changeable flow hydraulic machine.It is more particularly related to turn outside a kind of changeable flow
Sub- pump, such as gear pump or lobe pump, for liquid Ru Shui and oil.
Background technology
" hydraulic machine " means the device for being changed between fluid energy and mechanical energy.This can be along either one
To that is, can or can be to mechanical energy from fluid for motor from mechanical energy to fluid for pump.
Variable flow pump is known in the art.Such pump can change theirs independently of their powered speed
Output.Therefore, variable flow pump can for example, by vehicle motor (running speed of the vehicle motor and demand pump without
Close) to directly drive, while keep exporting according to the required pressure of the oil duct (oil gallery) for example in vehicle.
Therefore, the large change of the speed of service of pump will not cause the similar change of system oil pressure.
A variety of positive-displacement pumps as is generally known in the art.One example is gear pump, wherein, the cavity between the tooth of gear is used
In causing fluid outlet is moved to from import.External gear pump includes two gears engaging, reversely rotating, and they are contained in shell
In internal pump cavity.Semicircular surface is arranged in the outside of gear, and when gear teeth moves, the semicircular surface is sealed against
The tip of gear teeth.Import is positioned at the side of gear train, exports in opposite side.Gear, which is rotated into, causes tooth around the outer of pump cavity
Side moves to outlet from import, defeated from import in the cavity being formed between tooth and surface of shell so as to the fluid of limited capacity
Deliver to outlet.Because gear teeth engages, therefore when they return to import from outlet, considerably less high-pressure outlet fluid moves back to
Import.
The pump (internal gear pump or drum pump) of optional type uses first gear, and the first gear is mounted for second
Gear internal rotation, rotation axis and the second gear of first gear deviate, and have less tooth.The side of first gear and second
Gear engages.
Changeable flow internal gear pump is known in the art.A kind of changeable flow internal gear pump is in open source literature GB2445243
Disclosed in, wherein, there is provided two adjacent rotors of internal gear pump, a rotor has movable axis, to change pump
Flow velocity.
Another type of positive-displacement pump is lobe pump.Lobe pump is similar with gear pump, except protuberance (tooth) does not engage.
The synchronization of rotor is realized by external device (ED) (such as gear-box).For the application, external gear pump and lobe pump are referred to as " outside
Impeller pump ".
Known variable flow internal gear pump may at non-loaded (i.e. low discharge) inefficient.External gear pump will not run into phase
Same problem.A kind of external gear pump is needed, wherein, flow can change independently of speed, hence in so that the advantages of changeable flow
Combined with the advantages of external gear pump mechanism.
The content of the invention
Above mentioned problem further relates to hydraulic motor (i.e. wherein, working fluid is used to drive mechanical output shaft).Therefore, it is of the invention
Purpose be to provide a kind of improved changeable flow hydraulic machine.
According to the present invention, there is provided a kind of changeable flow outer rotor hydraulic machine, it includes：
Import；
Outlet；
Rotor set, the rotor set have be mounted for around the first rotor axis rotation the first rotor and be mounted for around
Second rotor of the second rotor axis rotation, the rotor set are arranged to：
(i) when activated, fluid is pumped to outlet from import；Or
(ii) driven by the working fluid for leading to outlet from import；
Wherein, in the first and second rotor axis it is at least one can relative to another motion, to change in rotor
Between leakage flow.
Advantageously, moved by the relative position of rotor, leakage flow between them can be changed, therefore
Net flow and outlet pressure can be changed.As described above, machine could be arranged to pump or motor.
Preferably, the first rotor axis is static that second rotor axis are movable.This causes the first rotor to be easier by outer
Portion's power source drive, or machine power is passed into single axle.Second rotor can be driven that (i.e. it is lazy by the first rotor
Wheel).
Preferably, changeable flow outer rotor hydraulic machine includes：
Housing；And
Carrier, the carrier can be relative to housing motions；
Wherein, movable rotor is arranged on carrier.
This enables carrier to provide in face of the surface of movable rotor, wherein, movable rotor and surface engagement, so as to
Fluid is pumped to outlet (or being rotated when machine is motor by working fluid) from import.
Preferably, carrier is rotatably installed in housing.This causes simple and firm structure, and it is than sliding carrier more
It can not possibly block.
In one embodiment, it is arranged so that carrier movement provided with linear actuator, the linear actuator.Carrier can be with
There is carrier axis, wherein, linear actuator is arranged to that (such as opposite end of carrier) is applied to carrier at interval with carrier axis
Reinforcing.Due to fault secure reason, carrier, which may be preferred that, is resiliently biased to maximum stream flow state.
Preferably, linear actuator is hydraulic actuator.
Hydraulic actuator can be controlled by control valve, and the control valve is driven by the pressure in pump discharge downstream.Control valve
It can be driven by the pressure of outlet downstream, to form closed-loop control.Control valve can be arranged to the stream using outlet downstream
Move to hydraulic actuator and power is provided.
In an alternative embodiment, carrier can be formed together with housing in carrier, opposite with movable rotor side
Carrier pressure chamber, wherein, the pressure in the position response carrier pressure chamber of carrier.Therefore, carrier can include seal area
Domain, for being sealed against the respective surfaces of housing.At least one in the sealing area of carrier and the respective regions of housing can be with
Including circular section surface, there is the geometric center on carrier rotational axis line.
Preferably, it is at least one including seal in the sealing area of carrier and the respective regions of housing.
Preferably, the sealing area of carrier is spaced apart to carrier axis so that chamber is as big (so as to increase as possible
Pressure on carrier).
Preferably, pressure chamber includes flow channel, for controlling pressure therein.Pressure in pressure chamber can be with
Controlled by control valve, the control valve is driven by the pressure in pump discharge downstream.Control valve can by the pressure of outlet downstream Lai
Driving, therefore form closed-loop system.
Preferably, control valve is arranged to be supplied to pressure chamber using the flowing of outlet downstream.
According to the second aspect of the invention, there is provided a kind of method for controlling the flow in outer rotor hydraulic machine, it is wrapped
Include following steps：
Outer rotor hydraulic machine is provided, the outer rotor hydraulic machine has rotor set, and the rotor set is positioned at inlet and outlet
Between, rotor set has the first rotor for being mounted for rotating around the first rotor axis and is mounted for around the second rotor axis
Second rotor of rotation；
(i) the first and second rotors are rotated around their respective axis, so as to which fluid is pumped into outlet from import；
Or
(ii) high-pressure fluid is provided in entrance, to cause the first and second rotors around them when fluid leads to outlet
Respective axis rotation, to produce mechanical output；And
Moved by one or two in the first and second rotor axis relative to another and change hydraulic press
The output of device.
It should be known that any of the above-described aspect of the present invention or preferably/optional feature can be used for hydraulic pump or hydraulic pressure horse
Reach.
Brief description of the drawings
The example variable flow pump according to the present invention is introduced below with reference to the accompanying drawings, in accompanying drawing：
Fig. 1 a are the partial cross-sectional side-elevation view in the first working condition according to the first pump of the present invention；
Fig. 1 b are partial cross-sectional side-elevation view of Fig. 1 a pump in the second working condition；
Fig. 2 a are using the first control program, the schematic diagram of Fig. 1 a pump；
Fig. 2 b are come the hydraulic circuit diagram of pump control, Fig. 1 a according to Fig. 2 a；
Fig. 3 is using the second control program, the schematic diagram of Fig. 1 a pump；
Fig. 4 is the side view according to the second pump of the present invention；
Fig. 5 a are using the first control program, the schematic diagram of Fig. 4 pump；
Fig. 5 b are come the hydraulic circuit diagram of pump control, Fig. 4 according to Fig. 5 a；And
Fig. 6 is using the second control program, the schematic diagram of Fig. 4 pump.
Embodiment
With reference to figure 1a and 1b, changeable flow external gear pump 10 is illustrated in figure, the changeable flow external gear pump 10 includes shell
Body 12, drive gear assemblies 14, driven gear component 16 and changeable flow control actuator 18.
Housing 12 includes body 20, and the body 20 is determined at pump cavity 22 and actuator cavity 24 therein.Pump cavity
22 determine：Import 26, the import 26 connect with external source of fluid (not shown)；Outlet 28, the outlet 28 will be passed with being used for
The regional fluid connection of the charging fluid sent；And a pair of relative gear cavities 30,32, this to gear cavity 30,32 side by side
Ground is positioned between import 26 and outlet 28.The local gear pump by semi-circular section of first gear cavity 30 contacts surface 34 come boundary
It is fixed.Second gear cavity 32 is local to be defined by carrier side to surface 36, and the carrier side is also substantially semi-circular to surface 36, but
It is that radius ratio gear pump contact surface 34 is big.
Carrier rotating dog, which is provided with, at first end of the carrier side to surface 36, close import 26 receives configuration 38.By
Female seat region 39 is provided with nearly outlet 28 of the carrier side to surface 36, the female seat region 39 depicts circle segments, and
There is the geometric center consistent with the center that carrier pin joint receives configuration 38.It is convex that sealing area 39 terminates at the carrier to extend radially outwardly
Ear cavity 40, the carrier lug cavity 40 have the first wall 41 and the second opposite wall 43.
Actuator cavity 24 includes cylinder holes 42, and the cylinder holes 42 is opened on the outside of housing 12 at one end.Fluid passage 44
Hull outside is extended radially outwardly to from cylinder holes 42 (cylinder holes 42 is in fluid communication with the fluid passage 44).The extension of cylinder holes 42 terminates
In convex shoulder 46, the convex shoulder 46 leads to push rod axis hole 48, and the push rod axis hole 48 is in the end relative with cylinder holes 42 and carrier lug
Cavity 40 connects, and the carrier lug cavity 40 is open through the second wall 43.In the opposite side of carrier lug cavity 40 (from the first wall
41 extensions) return spring cavity 50 is provided with, the return spring cavity 50 is also cylinder, and alignd with push rod axis hole 48.
Drive gear assemblies 14 include drive shaft 52, and the drive shaft 52 extends from the outside of housing 12, so as to by for example from
The drive shaft driving of internal combustion engine.The drive gear 54 being additionally provided with drive shaft 52, the drive gear 54 have circular body
56, the circular body 56 has multiple gear teeth 58, and these gear teeth 58 are respectively since the circular body 56 extends radially to tip 60.
Root 62 is provided between each gear teeth 58.
Driven gear component 16 includes carrier 64, idler shaft 66 and driven gear 68.
Carrier 64 is crescent body, and the crescent body is substantially semi-circular, is extended from the end of first end 70 to the second 72
Pass through 180 degree circular arc.Gear pump contact surface 78 is provided with radially towards inner side in carrier 64, gear pump contact surface 78 is half
Circle, and radius contacted with gear pump surface 34 radius it is similar.In carrier 64 surface is faced radially towards outside provided with housing
80.At first end 70, carrier 64 includes carrier rotating dog and receives configuration 74.At the second end 72, carrier 64 determines
Housing supporting surface 65, the housing supporting surface 65 depicts convex circle section, and is protruded from housing in face of surface 80.Comprising radially
Seal recess 84 towards outside seal 86 is arranged in supporting surface 65.The lug 76 to extend radially outwardly is arranged at carrier 64
The second end 72 at.The lug 76 determines semicircle ball-and-socket 82.
The idle pulley axle support structure (invisible) extended radially inwardly from carrier 64 is additionally provided with, the idle pulley axle support structure branch
Hold idler shaft 66.Idler shaft is mounted to contact surface 78 with gear pump to be rotated with one heart.As shown in Figure 1 a and 1b, driven gear
68 are supported on idler shaft 66.Driven gear 68 includes body 88, and the body 88 has multiple gear teeth to extend radially outwardly
90, the gear teeth 90 each own sophisticated 92 and the root 94 being determined between them.
Actuator 18 includes piston 96 and from the axially extending push rod 98 of the piston.Additionally provide closure 100.Actuator
18 also include return spring 102 and ball (ball bearing) 104.
The assembling of pump 10 is as follows.
Drive gear assemblies 14 are attached in housing 12, to drive the drive gear 54 in the inward turning of first gear cavity 30
Turn.Therefore, drive shaft 52 is mounted for contacting the Concentric rotation of surface 34 with gear pump, so that when gear 54 rotates, tooth 58
Tip 60 in the case where gap is minimum or very close to each other along contact surface 34 move.Gear 54 is arranged in the counterclockwise direction
Rotation, so as to which gear teeth 58 rotates around contact surface 34 towards exporting 28 on the contrary from import 26 and driven gear 88.
Driven gear component 16 is arranged in second gear cavity 32.Carrier 64 is arranged on carrier rotating dog 106, the load
Body rotating dog 106 receives configuration 38 with the carrier rotating dog on housing simultaneously and the carrier pin joint on carrier 64 receives configuration 74
Engagement.Therefore, carrier 64 is mounted for rotating around carrier pin axis C.
Carrier causes seal 86 to be skimmed over along female seat region 39 around axis C motion.Compare Fig. 1 a and 1b, carrier table
It is shown as being in first position in fig 1 a and (is revolved in the counterclockwise direction around axis C in the second diverse location in Figure 1b
Turn).
Driven gear 68 is arranged on idler shaft 56, so as to which when gear 68 rotates, the tip 92 of tooth 90 is minimum in gap
Or it is very close to each other in the case of along contact surface 78 move.Because driven gear 68 be arranged on carrier 64 on, therefore carrier 64 around
Axis C rotation causes driven gear 68 to be moved between the position shown in Fig. 1 a and the position shown in Fig. 1 b.As can in Fig. 1 a
See, the tip 92 of the gear teeth 90 of driven gear 88 is close to the root 62 of drive gear 56.By comparing, in Figure 1b, gear
Become less engagement.In other words, the fortune that the distance between drive gear and the rotation axis of driven gear passes through carrier 64
Move and increase.
Carrier 64 is moved by applying relative to force on lug 76.This is realized by actuating assembly 18.
Piston 96 is positioned in cylinder 42, and closure 100 is used to seal the cylinder 42, to form hydraulic chamber.From passage
The hydraulic pressure of 44 (passage 44 supplies to cylinder 42) causes piston 96 to Fig. 1 a and 1b left side to move.The motion of piston 96 to push away
Bar 98 moves, and the push rod 98 promotes on the lug 76 of carrier 64, to make it be revolved in the counterclockwise direction around carrier rotational axis line C
Turn.
Return spring 102 is arranged to be supported on the recess 82 of ball 104 of carrier 64.Therefore, when hydraulic pressure is released from passage 44
When putting, piston 96 moves right towards closure 100, therefore reduces the power on lug 76.Therefore, in return spring 102
In the presence of power, carrier returns to its shown position in fig 1 a.
In the operating process of the gear pump of the structure shown in Fig. 1 a, by the engagement of tooth, drive gear 54 is along counterclockwise
The rotation in direction rotates while causing driven gear 68 along clockwise direction.Because each gear supports it during
Against corresponding contact surface, therefore the fluid of discrete volume will be captured between gear, and around the edge of gear pump and from import
26 are delivered to outlet 28.Once by their corresponding contact surface, tooth continues back to rotate towards import 26.It should be known that
Although some high-pressure fluids will be entrained in the backstroke between export and import gear teeth and relative gear root it
Between, but these volume ratios multiple gear teeth and contact surface between large volume it is much smaller, therefore have from import 26 to
The net pumping effect of outlet 28.
With reference to figure 1b, when carrier 64 rotates in the counterclockwise direction around axis C, the axis of driven gear is away from drive gear
Axial-movement, so as to increase the spacing between the tip 92 of the tooth 90 of driven gear and the root 62 of drive gear.Therefore,
The gap formed between meshed gears allows more fluid to move to import 26 from outlet 28, and reduces the net pump of gear pump
Send effect.So, changeable flow is realized by the position of control vector 64, and this is just controlled between the axis of two gears
Distance.
With reference to figure 2a, gear pump 10 assembled with control valve 200, Fig. 1 a and 1b is illustrated in figure.Control valve 200 is to show
Meaning form represents.Control valve 200 is the guiding valve with two positions 202,204.(valve represents in an intermediate position, at this
In position, whole valve ports all block.)
Guiding valve 200 has return spring 208 and pressure face 210.Spring 208 and the Fluid pressure arrangement on pressure face 210
Into in a known way guiding valve 200 is moved between two positions 202,204 in opposite direction.
Control valve 200 has：
Control mouth CP, control mouth CP connect in an axial end portion of guiding valve with pressure face 210；
A mouthful AP is actuated, this actuates mouthful AP and connected with the first side of guiding valve 200；
Notch (tank port) TP, notch TP and guiding valve 200 the first fluid communication；And
Supply mouth FP, supply mouth FP and the actuator 18 of pump 10 passage 44 are in fluid communication.
In Fig. 2 a embodiment, control mouth CP is in fluid communication with mouthful AP is actuated.Both with the downstream of outlet 28 of pump 10
Fluid pressure zones connection.
When the pressure at control mouth CP is relatively low, guiding valve 200 is pushed into position 204 by spring 208.Supply mouth FP and groove
Mouth TP connections, therefore the low pressure at passage 44 enables spring 102 to push piston 96 to right-most position.In the state
In, pump is in maximum stream flow, and for increasing at outlet 28 pressure of (therefore at control mouth CP).
When the pressure increase at control mouth CP, guiding valve 200 moves right, so as to compression spring 208.This causes valve
200 move to position 202, wherein, actuate mouthful AP and be connected with supply mouth FP.This by the passage 44 of high-pressure fluid supply pump 10, with
Just so that piston 96 is to left movement.This compression spring 102, and carrier 64 is moved (i.e. from figure in the counterclockwise direction around axis C
1a to 1b).This have so that gear separation, so as to control outlet 28 at pump pressure effect.
Pressure at control mouth CP, which reduces, will cause guiding valve back to move to position 204, and in the position 204, cylinder is (living
Plug 96 is set within the tube) it is connected by supply mouth FP with notch TP, and pump output increase.
So, gear pump 10 is controlled by control pressure P.
This representation is hydraulic circuit diagram in figure 2b, therefore, control mouth P and actuates mouth under throttling arrangement R
Trip is in fluid communication with oil duct G.For example, oil duct G can be the passage for leading to vehicle bearing.In this case, throttling arrangement is
Into the entrance of the passage.
Structure shown in Fig. 2 b carrys out controlling pump 10 using oil duct pressure and actuates its controlling organization (into the shape of piston 96
Formula).
With reference to figure 3, there is provided a kind of optional hydraulic circuit, wherein, common elements with the portion shown in Fig. 2 a and 2b
Part identical reference number represents.In figure 3, control mouth CP is still connected in (i.e. throttling arrangement R downstream) with oil duct G.But,
Actuate the upstream that mouthful AP is immediately follows connected to the downstream, i.e. throttling arrangement R of outlet 28.
Pressure at outlet 28 is higher than oil duct pressure G (due to throttling arrangement R), and causes carrier 64 quickly to move
(compared with when oil duct pressure G is used to actuate cylinder 42).
With reference to figure 4, the alternative embodiment 10' of gear pump 10 is illustrated in figure.Gear pump 10' is very similar to gear pump
10, except difference described below.Gear pump 10' includes housing 12', drive gear assemblies 14' and driven gear component
16'.Gear assembly 12', 14' are arranged in gear cavity 22'.Import 26' leads in the outlet of the opposite side of gear pump structure
28'。
Carrier 64' is provided, carrier 64' is similar with carrier 64, extends to the second end 72' from first end 70', and install
On carrier rotating dog 106', for being rotated around axis C'.Carrier 64' determines the convex bearing surface with seal 86'
65', seal 86' meet the concave bearing surface 39' in housing 12'.Convex bearing surface 65' and concave bearing surface
39' has same radius, there is the geometric center consistent with carrier rotational axis line C'.
Therefore, variable carrier pressure chamber 302' is formed at carrier 64' load of the housing in face of surface 80' and housing 12'
Dignity is between the 36' of surface.Chamber 302' the pin 106' by the first end 70' in carrier and the second end 72' in carrier 64'
The seal 86' at place is sealed.
Although carrier 64' includes the lug 76' radially extended, the lug is not driven.It is only intended to pass through
Carried out against against surface 41', 43' with opposite carrier lug and limit carrier lug cavity 40's of the carrier 64' in housing 12'
Interior stroke.
Difference between pump 10' there is provided in the fluid passage 300' at carrier contact surface 36', the fluid
Passage 300' connects with carrier pressure chamber 302'.Actuating for carrier 64' leads to chamber by controlling by passage 300'(
Pressure 302') provides.Pressure increase in chamber 302' will force the housing to carrier 64' to apply in face of surface 80'
Net pressure, so that it is rotated in a clockwise direction around axis C'.Pressure in chamber 302', which reduces, will cause in carrier
Net pressure on 64', to cause it to be rotated in the counterclockwise direction around axis C'.Therefore, increasing pressure in chamber 302' will increase
The pressure being added at outlet 28, vice versa.
In fig 5 a it can be seen that an example of pump 10' operation, wherein, guiding valve 400 represents there is two positions
402nd, 404, return spring 408 and pressure face 410.Identical with valve 200, valve 400 is provided with：Control mouth CP, control mouth CP and pressure
Power face 410 is in fluid communication；Actuate a mouthful AP；Supply mouth FP, supply mouth FP are connected with the passage 300 ' of pump 10 '；And discharge groove
Mouth TP.
Pressure at control mouth CP always obtains in the downstream of outlet 28, to ensure closed-loop control.In the embodiment
In, control mouth CP obtains with mouthful FP is actuated from identical point.
When the pressure at control mouth CP is relatively low, guiding valve 400 is pushed into the second place 404 by spring 208.Supply mouth FP
Connected with actuating a mouthful AP, therefore, the high pressure at the place of passage 300 ' will push carrier 64 ' along clockwise direction, so that gear
Closer to.In this case, pump is in maximum stream flow, and for increasing at outlet 28 (and therefore at control mouth CP)
Pressure.
When the pressure rise at control mouth CP, the pressure increase on the pressure face 410 of guiding valve 400, valve moves to
First position 402.This causes passage 300 ' to be connected with outlet TP, and this just discharges the pressure in chamber 302 '.Across carrier
64 ' pressure differential causes it to rotate in the counterclockwise direction, therefore increases the separation between two meshing gears, so as to reduce
Export the pressure at 28 ' places.Therefore, the pressure at control mouth CP is controlled.
When the pressure decline at control mouth CP is too many, guiding valve 400 is finally back in the presence of return spring 408
The second place 404.
This system representation be Fig. 5 b in hydraulic circuit diagram, wherein, it can be seen that outlet 28 ' and pressure oil duct G it
Between have throttling arrangement R, it be used as control and actuating pressure.
With reference to figure 6, the alternative embodiment of the control system related to pump 10 ' is illustrated in figure, wherein, oil duct pressure is used for
It is controlled at the pressure face 410 of valve 400.It and can be used as without using oil duct pressure G and actuating the inlet-pressure at mouthful AP
Power (so as to the position of control vector 64 '), but use outlet pressure 28 '.
A variety of changes are fallen within the scope of the present invention.
As described above, embodiment described above and their each feature can be used in hydraulic motor (rather than
Pump).In this case, when fluid flows to low tension outlet, high-pressure inlet forces rotor to rotate, to drive mechanical output
Axle.For control program, in which case it is possible to use the distance between Electronic Control rotor, so that control machinery exports
Power.
Although working fluid is usually liquid (i.e. hydraulic pressure), it can also be gas (i.e. pneumatic).
The machine of the present invention can be reversible.For hydraulic pump, it may be desirable to so that the rotation of driving rotor is reverse, with
Just fluid is pumped in opposite direction.This falls within the scope of the present invention.
Different promoting methods can be used for the position of control vector.Linear electrical actuator can be used for so that carrier is transported
It is dynamic, instead of hydraulic actuator 18.Rotary actuator (such as electric notor) can directly drive the rotation of carrier 64.
Carrier need not be rotatable, such as it can be slided from and towards drive gear, however, it is to be understood that
Rotary system is substantially more reliable and simple.
The number of gear teeth and the property of rotor can change according to purposes.For example, replace with driving and from turn
Son, two rotors can have protuberance (such as in lobe pump), and can include certain form of external sync system, be used for
Ensure that they rotate in a suitable manner, so as to by fluid from import supply outlet.
Two rotors can all be driven, or vector rotor can be driven, rather than stationary rotor is (although this is more multiple
It is miscellaneous).
Two rotors can move, to change the distance between their axis.
Tri-rotor pump can be provided with center by driving rotor and two idle pulleys in either side.In this case, one
Or two idle pulley rotors can move relative to center rotor, to change flow.
Claims (13)
1. a kind of changeable flow outer rotor hydraulic machine, including：
Housing, the housing include pump cavity, and the pump cavity limits inlet and outlet；
Rotor set, the rotor set have be mounted for around the first rotor axis rotation the first rotor and be mounted for around
Second rotor of the second rotor axis rotation, the rotor set are arranged to：
(i) when activated, fluid is pumped to outlet from import；Or
(ii) driven by the working fluid for leading to outlet from import；
Wherein, in the first rotor axis and the second rotor axis it is at least one can relative to another motion, to change
Leakage flow between the first rotor and the second rotor；And
Carrier, the carrier can be relative to housing into rotation；
Wherein, the second rotor is arranged on carrier,
Carrier includes facing bitrochanteric surface,
Carrier forms the pressure chamber of carrier together with housing in carrier relative to the opposite side of the second rotor, wherein, carrier
Position response carrier pressure chamber in pressure and pump cavity in pressure.
2. changeable flow outer rotor hydraulic machine according to claim 1, wherein：The first rotor axis is static, second turn
Sub- axis is movable.
3. changeable flow outer rotor hydraulic machine according to claim 2, wherein：The first rotor and axis connection, the axle
It is arranged to：
(i) input shaft driven by external power supply；Or
(ii) output shaft；
Wherein, the second rotor is idle pulley.
4. changeable flow outer rotor hydraulic machine according to claim 1, wherein：Carrier includes sealing area, for close
Seal the respective surfaces against housing.
5. changeable flow outer rotor hydraulic machine according to claim 4, wherein：The sealing area of carrier and the phase of housing
Answer at least one including circular section surface in region, the circular section surface has in the geometry on carrier rotational axis line
The heart.
6. the changeable flow outer rotor hydraulic machine according to claim 4 or 5, wherein：The sealing area and housing of carrier
Respective regions in it is at least one including seal.
7. the changeable flow outer rotor hydraulic machine according to claim 4 or 5, wherein：The sealing area and carrier of carrier
Axis is spaced apart.
8. changeable flow outer rotor hydraulic machine as claimed in any of claims 1 to 5, wherein：Pressure chamber wraps
Flow channel is included, for the pressure in control pressure chamber.
9. changeable flow outer rotor hydraulic machine according to claim 8, wherein：Pressure in pressure chamber is by controlling
Valve controls, and the control valve drives by the pressure of outlet downstream.
10. changeable flow outer rotor hydraulic machine according to claim 9, wherein：Control valve by outlet downstream pressure
To actuate.
11. changeable flow outer rotor hydraulic machine according to claim 9, wherein：Control valve is arranged to using under outlet
The flowing of trip to carry out feed to pressure chamber.
12. changeable flow outer rotor hydraulic machine according to claim 10, wherein：Control valve is arranged to using under outlet
The flowing of trip to carry out feed to pressure chamber.
13. a kind of method for controlling the flow in outer rotor hydraulic machine, comprises the following steps：
Housing is provided, the housing includes pump cavity, and the pump cavity limits inlet and outlet；
Outer rotor hydraulic machine is provided, the outer rotor hydraulic machine has rotor set, and the rotor set is positioned at import and gone out
Between mouthful, rotor set has the first rotor for being mounted for rotating around the first rotor axis and is mounted for around the second rotor
Second rotor of axis rotation；
There is provided can be relative to the carrier of housing into rotation, and the carrier includes facing bitrochanteric surface；
Wherein, carrier forms carrier pressure chamber in carrier together with housing relative to the opposite side of the second rotor；
(i) the first rotor and the second rotor are rotated around their respective axis, so as to which fluid is pumped into outlet from import；
Or
(ii) high-pressure fluid is provided in entrance, to cause the first rotor and the second rotor around them when fluid leads to outlet
Respective axis rotation, to produce mechanical output；And
Moved by one or two in the first rotor axis and the second rotor axis relative to another, change response
The position of the carrier of pressure in carrier pressure chamber and the pressure in pump cavity, so as to change the defeated of outer rotor hydraulic machine
Go out.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB1315916.5 | 2013-09-06 | ||
| GB1315916.5A GB2517966B (en) | 2013-09-06 | 2013-09-06 | Variable flow hydraulic machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104421149A CN104421149A (en) | 2015-03-18 |
| CN104421149B true CN104421149B (en) | 2018-02-23 |
Family
ID=49486853
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410450027.0A Active CN104421149B (en) | 2013-09-06 | 2014-09-05 | Changeable flow hydraulic machine |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US9752572B2 (en) |
| CN (1) | CN104421149B (en) |
| GB (1) | GB2517966B (en) |
| IN (1) | IN2014DE02437A (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN209033764U (en) | 2015-04-06 | 2019-06-28 | 特灵国际有限公司 | Active clearance management in helical-lobe compressor |
| DE202015105177U1 (en) * | 2015-09-30 | 2017-01-02 | Ebm-Papst St. Georgen Gmbh & Co. Kg | Arrangement for determining a pressure |
| CN107762718B (en) * | 2016-08-16 | 2020-03-17 | 博罗承创精密工业有限公司 | Pneumatic motor |
| WO2019094386A1 (en) | 2017-11-08 | 2019-05-16 | Johnson Controls Technology Company | Variable compressor housing |
| CN109026162B (en) * | 2018-07-16 | 2019-08-16 | 朱三立 | A kind of screw expansion (compression) machine with variable volume ratio |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1602740A (en) * | 1924-11-18 | 1926-10-12 | Bechler Andre | Gear-wheel pump |
| US1704704A (en) * | 1927-08-08 | 1929-03-12 | Albert E Grant | Gear pump |
| US2606503A (en) * | 1946-01-11 | 1952-08-12 | Worthington Corp | Variable capacity rotary pump |
| US2754765A (en) * | 1949-01-29 | 1956-07-17 | Joy Mfg Co | Variable displacement pump |
| US2895422A (en) * | 1955-06-02 | 1959-07-21 | Gold Harold | Variable displacement fluid pump or motor |
| US2948228A (en) * | 1956-04-17 | 1960-08-09 | Svenska Rotor Maskiner Ab | Gear arrangement functioning as pump or motor |
| US3107629A (en) * | 1960-03-14 | 1963-10-22 | Reiners & Wiggermann Getriebe | Controllable gear-type hydraulic machine |
| US3782114A (en) * | 1972-03-24 | 1974-01-01 | Stradco Inc | Hydraulic propulsion system |
| US4531898A (en) * | 1983-12-13 | 1985-07-30 | Nissan Motor Co., Ltd. | Control system for a vane type variable displacement pump |
| US6983680B2 (en) * | 2002-08-28 | 2006-01-10 | Torvec, Inc. | Long-piston hydraulic machines |
| WO2006045190A1 (en) * | 2004-10-25 | 2006-05-04 | Magna Powertrain Inc. | Variable capacity vane pump with force reducing chamber on displacement ring |
| DE102007051349A1 (en) * | 2007-10-26 | 2009-04-30 | Robert Bosch Gmbh | Hydraulic gear machine e.g. external gear pump, for e.g. generating hydraulic energy, has actuator device to adjust axis position during machine operation and working against shaft deflection forces, where shafts center distance is changed |
| JP5174720B2 (en) * | 2009-03-09 | 2013-04-03 | 日立オートモティブシステムズ株式会社 | Variable displacement pump |
| JP5278779B2 (en) * | 2010-12-21 | 2013-09-04 | アイシン精機株式会社 | Oil pump |
| JP5620882B2 (en) * | 2011-05-23 | 2014-11-05 | 日立オートモティブシステムズ株式会社 | Variable displacement pump |
-
2013
- 2013-09-06 GB GB1315916.5A patent/GB2517966B/en active Active
-
2014
- 2014-08-27 IN IN2437DE2014 patent/IN2014DE02437A/en unknown
- 2014-09-05 CN CN201410450027.0A patent/CN104421149B/en active Active
- 2014-09-05 US US14/478,111 patent/US9752572B2/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| IN2014DE02437A (en) | 2015-06-26 |
| US9752572B2 (en) | 2017-09-05 |
| GB2517966B (en) | 2020-05-20 |
| CN104421149A (en) | 2015-03-18 |
| US20150071804A1 (en) | 2015-03-12 |
| GB2517966A (en) | 2015-03-11 |
| GB201315916D0 (en) | 2013-10-23 |
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